US9217506B2 - Actuation device for actuating switching elements - Google Patents

Actuation device for actuating switching elements Download PDF

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Publication number
US9217506B2
US9217506B2 US14/352,104 US201214352104A US9217506B2 US 9217506 B2 US9217506 B2 US 9217506B2 US 201214352104 A US201214352104 A US 201214352104A US 9217506 B2 US9217506 B2 US 9217506B2
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Prior art keywords
shifting
valve
shut
actuating device
actuating
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Expired - Fee Related
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US14/352,104
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US20140230591A1 (en
Inventor
Matthias Reisch
Ralf Dreibholz
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ZF Friedrichshafen AG
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ZF Friedrichshafen AG
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Assigned to ZF FRIEDRICHSHAFEN AG reassignment ZF FRIEDRICHSHAFEN AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DREIBHOLZ, RALF, REISCH, MATTHIAS
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/68—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for stepped gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/04—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube
    • F16D25/042—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube the elastic actuating member rotating with the clutch
    • F16D25/044—Fluid-actuated clutches in which the fluid actuates an elastic clutching, i.e. elastic actuating member, e.g. a diaphragm or a pneumatic tube the elastic actuating member rotating with the clutch and causing purely axial movement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F16D25/0638—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs with more than two discs, e.g. multiple lamellae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D48/0206—Control by fluid pressure in a system with a plurality of fluid-actuated clutches
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K11/00—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection
    • H02K11/0094—Structural association with other electrical or electronic devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0221—Valves for clutch control systems; Details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D2048/0257—Hydraulic circuit layouts, i.e. details of hydraulic circuit elements or the arrangement thereof
    • F16D2048/0278—Two valves in series arrangement for controlling supply to actuation cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2708/00—Control devices for speed-changing geared mechanisms, e.g. specially adapted couplings for synchronising devices, devices to simplify control, control of auxiliary gearboxes
    • F16H2708/16—Control devices for speed-changing geared mechanisms, e.g. specially adapted couplings for synchronising devices, devices to simplify control, control of auxiliary gearboxes wherein the gearing is not described or not essential
    • F16H2708/20—Control devices for speed-changing geared mechanisms, e.g. specially adapted couplings for synchronising devices, devices to simplify control, control of auxiliary gearboxes wherein the gearing is not described or not essential the control being hydraulic or pneumatic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2708/00—Control devices for speed-changing geared mechanisms, e.g. specially adapted couplings for synchronising devices, devices to simplify control, control of auxiliary gearboxes
    • F16H2708/16—Control devices for speed-changing geared mechanisms, e.g. specially adapted couplings for synchronising devices, devices to simplify control, control of auxiliary gearboxes wherein the gearing is not described or not essential
    • F16H2708/22—Control devices for speed-changing geared mechanisms, e.g. specially adapted couplings for synchronising devices, devices to simplify control, control of auxiliary gearboxes wherein the gearing is not described or not essential the control being electric
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K16/00—Machines with more than one rotor or stator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19219—Interchangeably locked
    • Y10T74/19251—Control mechanism

Definitions

  • the invention relates to an actuating device for actuating at least one shifting element shiftable through a shifting device, along with the use of the actuating device.
  • shifting elements i.e. clutches or brakes, designed as multi-disk shifting elements or claw shifting elements.
  • shifting takes placing hydraulically, i.e. through shifting devices in the form of piston/cylinder units, which are coated with pressurized oil.
  • the pressurized oil is conveyed by a pump and through oil supplies of the transmission housing through so-called rotating oil feeds, into the rotating gear shaft, and led from it to the shifting devices.
  • Losses that burden the transmission efficiency arise from the hydraulic circuit, i.e. the performance of the transmission oil pump, seals, pressure drops in the supply lines, and leakage.
  • a hydraulically shiftable multi-disk shifting element is known from DE 102 05 411 A1 of the applicant, wherein in a closed state, i.e. upon the transmission of the turning moment, the multi-disk shifting element is mechanically locked by a locking device. Thereby, the contact force between the multi-disks is maintained, without hydraulic pressure having to act—the transmission oil pump is thereby unburdened.
  • the locking device is designed as a shut-off valve, which is arranged in the supply area of the hydraulic cylinder. Thus, the pressure space of the cylinder at the pump is shut off, and the necessary pressure is maintained for maintaining the contact pressure in the multi-disk pack.
  • the shifting element is closed, the transmission oil pump is unburdened.
  • a synchronization for a manual transmission is known from DE 10 2006 049 283 A1 of the applicant, whereas an idler gear is able to be shifted by means of an actuator arranged in a gear shaft, designed as a cylinder/piston unit.
  • the cylinder of the actuator features two pressurized medium lines, in which shut-off valves are arranged, through which the pressure prevailing in the cylinder can be maintained, without the pump having to consume power.
  • the task of the invention is to create an actuating device of the aforementioned type with the smallest possible losses, in particular upon use in transmissions. Additional objects and advantages of the invention will be set forth in part in the following description, or may be obvious from the description, or may be learned through practice of the invention.
  • the shut-off valve that maintains the closing pressure in the pressure space of the shifting device is connected in a torque-proof manner to at least one shifting element and is electrically controllable, whereas electrical energy is able to be supplied without contact.
  • the contact-free transmission of power preferably takes place on an inductive basis, whereas a fixed-location primary coil and a co-rotating secondary coil may be provided. This avoids plug connections and mechanical friction losses for the supply of power.
  • the shifting device is able to be actuated hydraulically or pneumatically, i.e. embodiments are not limited to only one pressurized medium.
  • the shifting device is designed as a bellows, which is able to be filled with a pressurized medium.
  • the bellows forms a closed pressure space, in which no seals are necessary. This results in the advantage of an absolute tightness and, through the discontinued use of sealing elements, an efficiency gain.
  • the closing pressure in the bellows is maintained by the shut-off valve.
  • At least one shifting device is designed as a piston/cylinder unit, which may be coated by a liquid or gaseous medium.
  • the piston is designed as an annular piston.
  • the shifting force generated by the shifting device may be transferred to the shifting element, for example a multi-disk clutch.
  • the shut-off valve forms a component or a part of an actuator, which also includes an electric motor and a valve spindle, which moves a valve closure element provided with a movement thread.
  • a relatively high closing pressure for the shut-off valve may be achieved through the spindle/nut drive.
  • the actuator also referred to as an actor
  • the actuator comprises a part of a drive—here, the electric motor—and a valve part (closed body)—here the valve closure element with a valve spindle.
  • the shut-off valve is a part of an actuator, which comprises a magnetic coil, an armature and a valve tappet, which actuates the valve closure element.
  • an actuator which comprises a magnetic coil, an armature and a valve tappet, which actuates the valve closure element.
  • an electronic control device also referred to as an electronics module
  • an electronics module is attached to at the at least one shifting element.
  • Electronic components such as a secondary coil for the contact-free transmission of power and parts of the actuator, are incorporated in the co-rotating electronics module.
  • the electronics module represents a unit that is pre-assembled to the greatest possible extent.
  • a functional mounting in which moving parts of the actuator are incorporated and are arranged in floating form in a hydraulic fluid, is connected to at least one shifting element. This achieves compensation for the centrifugal force.
  • the moving parts such as the valve spindle, armature shaft and valve closure element, experience a buoyant force, which is directed against the operating direction of the centrifugal force.
  • the average density of the moving parts approaches the average density of the hydraulic fluid, preferably a hydraulic or transmission oil.
  • This can be achieved, for example, through hollow construction (armature hollow shaft) or lightweight construction (plastic or light metal materials).
  • a power accumulator is provided in the power flow between the actuator and the shifting element; this mechanism has the function by compensating for a diminishing shifting force. This avoids any slipping of the shifting element, for example a multi-disk clutch.
  • the power accumulator may be designed as an elastic element, for example as a disk spring, and/or as an elastic annular piston.
  • fluid is supplied to the shut-off valve through a rotary signal transmitter, i.e. a device for delivering fluid from a fixed-location component to a rotating component.
  • a rotary signal transmitter i.e. a device for delivering fluid from a fixed-location component to a rotating component.
  • a single rotary signal transmitter provides fluid to several shut-off valves and shifting devices assigned to them, which reduces the number of rotary signal transmitters causing friction and leakage losses.
  • multiple shifting elements may be optionally actuated with only one pressure control valve or only one rotary signal transmitter.
  • the rotary signal transmitter is applied with a pressure level that corresponds to a lubrication pressure level, for example an oil pressure of 0.3 bar. This ensures that, with a closed pressure control valve, if there is no pressure on the rotary signal transmitter, the rotary signal transmitter does not draw any air bubbles. Air bubbles in the hydraulic system would impair reproducible control characteristics. In the case of a transmission, a lubrication pressure level is already available.
  • a contact-free position sensor with a displacement transducer and an acceptor, is allocated to the electronics module and at least one shifting device.
  • the displacement transducer may be arranged in an annular piston of a shifting device, such as a multi-disk clutch.
  • Pressure or force sensors can also be provided. Thereby, the respective operating status of the shifting element (open, closed or intermediate positions) can be recorded. The shift quality can thereby be improved, and a creeping pressure loss in the shifting device is detected and tracked, without this leading to a change to the driver conduct.
  • a pressure accumulator which is replenished by an intermittently running electric pump, is provided.
  • hydraulic fluid may be provided at a constant pressure level, and the driving power of the hydraulic pump may be reduced.
  • the actuating device described above is advantageously used in a transmission, in particular an automatic transmission for motor vehicles. This can improve the overall efficiency of the transmission.
  • FIG. 1 an axial section of an actuating device in accordance with the invention with a shut-off valve and shifting elements for a transmission
  • FIG. 2 a hydraulic circuit diagram for the actuation of shifting elements
  • FIG. 3 an electronics module for incorporating actuators.
  • FIG. 4 an axial section through the shifting elements with a contact-free position sensor
  • FIG. 5 a shifting device designed as a bellows as a further embodiment of the invention.
  • FIG. 1 shows an actuating device in accordance with the invention for an automatic transmission of a motor vehicle with a gear shaft 1 , on which a so-called functional mounting 2 with a rotational axis “a” is arranged in a torque-proof manner.
  • a total of three shifting elements namely a first multi-disk clutch 3 , a second multi-disk clutch 4 , and a claw coupling 5 , are connected to the functional mounting 2 .
  • Each of the shifting devices 6 , 7 features a ring-shaped ring cylinder designed as a pressure space 6 a , 7 a , which is arranged in the functional mounting 2 .
  • the shifting elements 3 , 4 , 5 are connected on the drive side through a common, combined multi-disk/claw carrier 9 that, regarding the first multi-disk clutch 3 , is designed as an outer multi-disk carrier 9 a , regarding the second multi-disk clutch 4 , is designed as an inner multi-disk carrier 9 b , and regarding the claw coupling 5 , is designed as a claw carrier 9 c .
  • the output side of the first multi-disk clutch 3 features an inner multi-disk carrier 3 a , which is connected to a cylinder-shaped output element 10 .
  • the claw coupling 5 is connected to a further cylinder-shaped output element 11 .
  • the second multi-disk clutch 4 features an outer multi-disk carrier 4 a , which forms the third output element 12 .
  • the first multi-disk clutch 3 is actuated through a first annular piston 13
  • the second multi-disk clutch 4 is actuated through a second annular piston 14
  • the claw coupling 5 is actuated through several shifting arms 15 arranged around the circumference of the functional mounting 2 .
  • the combined multi-disk/claw carrier 9 is connected in a torque-proof manner to the functional mounting 2 through a connecting element 16 , such that the drive sides of the three shifting elements 3 , 4 , 5 are connected to the gear shaft 1 through the functional mounting 2 .
  • the functional mounting 2 is also the mounting of the shifting elements 3 , 4 , 5 .
  • a shut-off valve 17 is arranged in the functional mounting 2 , which comprises two bodies 2 a , 2 b connected to each other.
  • This shut-off valve controls the pressurized oil supply to the pressure space 7 a of the shifting device 7 .
  • a so-called rotary oil feed 19 also referred to as a rotary oil exchanger 19 , is provided between a (schematically shown) transmission housing 18 and the gear shaft 1 ; i.e., the pressurized oil is passed from a fixed-housing channel 20 into an annular groove 21 in the gear shaft 1 .
  • the pressurized oil passes into an oil channel 25 of the functional mounting 2 , and from there to the shut-off valve 17 .
  • a pressurized oil channel 26 leads into the pressure space 7 a .
  • the pressurized oil supply to the additional pressure spaces 6 a , 8 a of the shifting devices 6 , 8 is shown in part with dotted lines—the associated shut-off valves are not visible in the sectional view, as they are arranged in a manner moving in a circumferential direction.
  • each shifting device 6 , 7 , 8 is equipped with a shut-off valve—as emerges below from the explanation of FIG. 2 .
  • the shut-off valve 17 is electrically actuated, in the embodiment shown by the electric motor 27 , which is arranged in an electronic control device 28 , designed in a ring shape, also referred to as an electronics module 28 .
  • the electronics module 28 which features additional functions, is the subject matter of a separate simultaneously filed patent application of the applicant with U.S. application Ser. No. 14/352,095. The subject matter of this simultaneous application is fully incorporated by reference in the disclosure content of this application for all purposes.
  • the shut-off valve 17 forms an actuator, also referred to as an actor.
  • the shut-off valve 17 features a rotating spindle 17 a and a valve closure element 17 b connected through it to a movement thread.
  • the rotating spindle 17 a is connected to a hollow shaft 17 c , on which an armature of the electric motor 27 (not shown with a reference number) is arranged.
  • the moving parts of the actuator such as the rotating spindle 17 a and the hollow shaft 17 c , which are arranged parallel to the axis of rotation “a”, are subject to a centrifugal force effect, and are therefore arranged in floating form in the pressurized oil, which generates a buoyant force directed against the centrifugal force.
  • the centrifugal force can be compensated for through the design of the movable valve components in terms of form and material.
  • the electronics module 28 receives its electrical energy and its signals for closing and opening the shut-off valve 17 on an inductive basis.
  • a primary coil 29 on the housing side i.e., fixed-location
  • a secondary coil 30 arranged in the rotating electronics module 28 are provided. Additional details of the electronics module 28 are explained in connection with the description of FIG. 3 .
  • the actuating device preferably features a power accumulator, which is arranged in the power flow between an actuator and/or a shut-off valve 17 and a shifting element 4 (and likewise between the other actuators and shifting elements), and acts as an energy reserve upon diminishing contact force in the multi-disk pack.
  • the power accumulator is formed as an elastic element, for example as a disk spring, whereas the disk spring may also be integrated into the annular piston 14 .
  • FIG. 2 shows a section from a hydraulic circuit diagram for the shifting devices 6 , 7 , 8 in accordance with FIG. 1 , which are allocated to the shifting elements 3 , 5 , 7 in accordance with FIG. 1 .
  • the shut-off valve 17 in accordance with FIG. 1 is allocated to the shifting device, i.e. the piston/cylinder unit 7 .
  • the shut-off valves 31 , 32 are allocated to the shifting devices 6 , 8 .
  • a rotary oil supply also referred to as a rotary signal transmitter
  • the oil transfer from the housing into the rotating gear shaft is designated.
  • An electromotive, intermittently driven transmission oil pump 33 conveys pressurized oil into a pressure accumulator 34 , from which the pressurized oil is supplied through the pressure control valves 35 , 36 to the rotary oil exchanger 19 and an additional rotary oil exchanger 37 .
  • the shifting device 6 is supplied by a separate rotary oil supply 37
  • the two shifting devices 7 , 8 are connected in parallel downstream of the rotary oil exchanger 19 ; i.e., they feature a common rotary oil exchanger 19 —thereby, an additional rotary oil exchanger fraught with losses can be spared.
  • each shifting device 6 , 7 , 8 is controlled by a separate shut-off value 31 , 17 , 32 , such that, if the clutch is closed, the closing pressure in the pressure space can be maintained, without the pressure accumulator 34 having to be tapped, or the pump 33 having to deliver power.
  • the rotary oil exchanger 19 , 37 is applied with lubricating oil pressure, so that they do not draw in any air bubbles. In the transmission, there is a lubricating oil pressure in the amount of approximately 1.5 bar.
  • FIG. 3 shows the electronics module 28 as a separate structural unit in a perspective view, whereas two shut-off valves, the shut-off valve 17 shown in FIG. 1 and an additional identical shut-off valve 38 are shown in sections.
  • the electronics module 28 features a housing 39 formed in a ring shape, which is sealed to the outside by a cover 40 .
  • the stator of the electric motor 27 is arranged inside the housing 39 (as in FIG. 1 , the same reference numbers are used for the same parts).
  • connection fittings 41 are molded, through which the electronics module 28 is connected to the body 2 a of the functional mounting 2 (see FIG. 1 ).
  • shut-off valves two with the reference numbers 17 , 38 , and two more without reference numbers, can be seen.
  • the rotating spindle 17 a and the hollow shaft 17 c run in oil.
  • they are subject to a centrifugal force effect and, on the other hand, they experience a buoyant force, which is determined by the weight of the quantity of the displaced oil.
  • the armature shaft 17 c is hollow.
  • the hollow shaft 17 c is mounted twice.
  • a magnet may also be used in connection with a valve tappet, depending on the type of magnetic valve.
  • the translational motion of the valve tappet is then directly transferred to the closure element.
  • the transmission of electrical energy is effected on an inductive basis.
  • the secondary winding 30 is arranged within the electronics module 28 in the radial internal area, which is in operative connection with the primary winding not shown here (see FIG. 1 ).
  • FIG. 4 shows an additional axial section through the functional mounting 2 and the shifting elements 3 , 4 (as in FIG. 1 , the same reference numbers are used for the same parts).
  • a contact-free position sensor 43 is arranged on the electronics module 28 , which operates, for example, according to the method of a differential transformer.
  • the position sensor 43 comprises a transducer pin 44 fixed on the annular piston 13 of the shifting element 3 , and an acceptor part 45 designed as a cup arranged on the electronics module 28 , in which the transducer pin 44 is immersed.
  • Several such position sensors may be arranged around the circumference of the electronics module 28 .
  • additional pressure and/or force sensors can be provided (which is not shown), the signals of which are incorporated by the electronic control device 28 .
  • FIG. 5 shows, as a further embodiment of the invention, a shifting element 46 with a multi-disk pack 47 , which, through a bellows 48 , receives the contact pressure necessary for the transmission of the turning moment.
  • the interior of the bellows 48 which is supported on the one hand on the multi-disk pack 47 , and on the other hand on the housing of the shifting element 46 , is filled with a pressurized medium, pressurized oil or pressurized air, via a supply line 49 .
  • a shut-off valve in accordance with the invention is arranged (which is not shown). If the coupling is closed, this valve maintains the closing pressure in the bellows 48 and thus provides for a transmission of a constant turning moment.
  • the bellows it is advantageous that there is no need for sealing elements in the form of piston rings or O-rings, and that no leakage occurs.
  • the bellows 48 can be directly incorporated into the shifting element 46 , which eliminates an annular piston and a pressure space in the functional mounting 2 (see FIG. 1 ).
  • the functional mounting is designed as a multi-functional mounting, and may take on even more functions, such as the incorporation of cooling oil and lubricating oil valves for controlling a cooling oil flow for the multi-disk shifting elements, which can thus be cooled according to need.
  • a lubricating oil valve arranged in the functional mounting is the subject matter of a simultaneously filed patent application of the applicant with U.S. application Ser. No. 14/352,095, which is hereby fully incorporated in the disclosure content of this application for all purposes.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Power Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Control Of Transmission Device (AREA)
  • Gear-Shifting Mechanisms (AREA)
US14/352,104 2011-10-17 2012-09-13 Actuation device for actuating switching elements Expired - Fee Related US9217506B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102011084583A DE102011084583A1 (de) 2011-10-17 2011-10-17 Betätigungseinrichtung zum Betätigen von Schaltelementen
DE102011084583 2011-10-17
DE102011084583.6 2011-10-17
PCT/EP2012/067912 WO2013056904A1 (de) 2011-10-17 2012-09-13 Betätigungseinrichtung zum betätigen von schaltelementen

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Publication Number Publication Date
US20140230591A1 US20140230591A1 (en) 2014-08-21
US9217506B2 true US9217506B2 (en) 2015-12-22

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US14/352,104 Expired - Fee Related US9217506B2 (en) 2011-10-17 2012-09-13 Actuation device for actuating switching elements

Country Status (6)

Country Link
US (1) US9217506B2 (de)
EP (1) EP2769110B1 (de)
JP (1) JP6131257B2 (de)
CN (1) CN103874864B (de)
DE (1) DE102011084583A1 (de)
WO (1) WO2013056904A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180259006A1 (en) * 2017-03-10 2018-09-13 Honda Motor Co., Ltd. Hydraulic clutch device

Families Citing this family (9)

* Cited by examiner, † Cited by third party
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DE102011084585A1 (de) * 2011-10-17 2013-04-18 Zf Friedrichshafen Ag Elektronische Steuereinrichtung zur Steuerung von Aktuatoren
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JP2014528560A (ja) 2014-10-27
JP6131257B2 (ja) 2017-05-17
DE102011084583A1 (de) 2013-04-18
EP2769110A1 (de) 2014-08-27
EP2769110B1 (de) 2017-08-09
WO2013056904A1 (de) 2013-04-25
CN103874864A (zh) 2014-06-18
CN103874864B (zh) 2019-03-29
US20140230591A1 (en) 2014-08-21

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